Rotary engine oil metering pump

ABSTRACT

A rotary engine is provided with an oil metering pump having a shaft rotatably mounted in the pump&#39;&#39;s body that is driven by the engine and has an expansible pump chamber which is contracted and expanded by a plunger that is mounted for reciprocal movement in a radial direction in the shaft. A ring arranged about the pump shaft effects reciprocating motion of the plunger as the shaft turns with the plunger stroke varied by varying the eccentricity of the ring in accordance with engine throttle opening. A single oil supply port in the pump&#39;&#39;s body is connected via an oil inletoil outlet port in the pump shaft to the pump chamber as the chamber is expanding as the shaft turns and this oil inlet-oil outlet port thereafter connects the chamber as it contracts to one oil delivery port in the pump&#39;&#39;s body and then another all during one complete pump shaft revolution.

United States Patent Palma et al.

[ Feb. 26, 1974 ROTARY ENGINE OIL METERING PUMP Primary Examiner-CarltonR. Croylc 75 Inventors: amen l). Palmu- Robert E. Mor n AsslsmmExaminer-Meme] P'J 1 g of Grand iiapids Mich. Attorney, Agent, orFirm-R. L. Ph1ll1ps [73] Assignee: General Motors Corporation, [57]ABSTRACT Dem)", Mlch- A rotary engine is provided with an oil meteringpump [22] Filed; No 0 72 having a shaft rotatably mounted in the pumpsbody that is driven by the engine and has an expansible [21] PP 308,050pump chamber which is contracted and expanded by a plunger that ismounted for reciprocal movement in a 5 s C]. U 123 9 R, 23 0 123 7 AD,radial direction in the shaft. A ring arranged about the 184/31, 417/22]pump shaft effects reciprocating motion of the plunger 51 Int. (:1...F01n 1/02, Fl6n 13/20 as the Shaft turns with the plunger Strokevaried y [58] Field of Search ..123/8.0l, 139 ED, 196 R, varying theeccentricity 9f the e in accordance with 123/73 AD; 417/220, 221;184/65, engine throttle opening. A single oil supply port in the 417/31,5; 9 /497 pumps body is connected via an oil inlet-oil outlet port inthe pump shaft to the pump chamber as the 5 References Cited chamber isexpanding as the shaft turns and this oil in- UNITED STATES PATENTSlet-oil outlet port thereafter connects the chamber as 2 it contracts toone oil delivery port in the pumps body I $23233 IIIIIIIIIIIIIIIIII 22 2and then another all during one complete pump shaft 3,140,700 7/1964Nallinger 123/196 R X revoluton' 3 Claims, 4 Drawing Figures W 87 I i W7 affilll w 70 4 ROTARY ENGINE OIL METERING PUMP This invention relatesto a rotary engine oil metering pump and more particularly to an oilmetering pump that meters oil to lubricate a rotary engines gas seals inaccordance with engine speed and throttle opening.

In a rotary engine, it is desirable to meter oil to lubricate the enginerotors gas seals at a rate that increases with engine load. One mannerof doing this is to meter the oil at a rate that increases withincreasing engine speed and torque demand as indicated by enginethrottle opening. While there are presently commercial pumps thatproduce such oil metering operation, there is a continuing effort forsimplification and reduction in size of the pump coupled with increasedreliability and reduction in cost.

The rotary engine oil metering pump according to the present inventionis directed to the above goals and comprises a pump body receiving arotary pump shaft that is drivingly connected to the engines shaft sothat it turns at a speed proportional thereto when the engine isrunning. The pump shaft has an oil chamber including a radial bore inwhich a plunger is mounted for reciprocal movement in a radial directionto vary the volume of the chamber. A ring is mounted in the pump bodyabout the pump shaft and has a radially inwardly facing circular controlsurface that is arranged opposite the plunger which is biased by aspring to remain in contact therewith as the shift turns. The ring isprevented from rotary movement while being permitted to move in oppositeradial directions relative to the pump shaft between positions where itis eccentric with respect to the pump shaft so that the plunger iscaused to reciprocate as the pump shaft turns with a stroke thatincreases with increasing eccentricity of the ring. A shaft mounted onthe pump body which moves axially when turned engages the stroke controlring and is controlled with the engine throttle to move the strokecontrol ring in a direction to increase the plunger stroke and thus pumpdisplacement as the engine throttle is opened. An oil supply passage inthe pump body supplies oil to be metered and a pair of oil deliverypassages in the pump body deliver the metered oil to lubrieats atwo-rotor engine. The pump body has an inlet recess cooperating with thepump shaft to provide an inlet port that is connected to the oil supplypassage and also has a pair of angularly spaced outlet recesses thatcooperate with the pump shaft to provide a pair of angularly spacedoutlet ports that are separately connected to the oil delivery passages.The oil chamber in the shaft has an oil inlet-oil outlet port thatduring a single pump shaft rotation connects the inlet port to the oilchamber as the chamber is expanding and then suc cessively connects theoil chamber to the outlet ports when the oil chamber is contracting.Thus, each of the oil delivery passages receives oil that is metered ata rate that increases with increasing engine speed and throttle valveopening.

An object of the present invention is to provide a new and improvedrotary engine oil metering pump.

Another object is to provide a rotary engine oil metering pump having ashaft that is driven by the engine and has an expansible chamber whichis contracted and expanded by a plunger that is reciprocally mounted onthe shaft and is cause to reciprocate by engagement with a surroundingring with a stroke varying with the eccentricity of this ring which iscontrolled with the engine throttle to provide an oil rate thatincreases with increasing engine speed and engine throttle opening.

Another object is to provide a rotary engine oil metering pump having ashaft that is engine driven and has an expansible chamber with a plungerwhich is operated by an eccentricly arranged ring whose eccentricity iscontrolled with engine throttle opening to effect pumping action with adisplacement that increases with increasing throttle opening and adisplacement per unit of time that increases with increasing enginespeed and with this oil being metered from a single oil inlet portsuccessively to two outlet ports during each pump shaft revolution.

These and other objects of the invention will become more apparent withreference to the following description and drawing in which:

FIG. 1 is an elevational view with parts shown diagrammatically andparts in section of a rotary engine having an oil metering pumpaccording to the present invention.

FIG. 2 is an enlarged view of the oil metering pump taken along the line2-2 in FIG. 1.

FIG. 3 is a view of the oil metering pump taken along the line 3-3 inFl(]. 2.

FIG. 4 is a view of the oil metering pump taken along the line 44 inFIG. 2.

Referring to FIG. I, there is shown a rotary combustion engine 10 ofcurrent production type having an oil metering pump 12 according to thepresent invention that meters oil to lubricate the engines gas seals.The engine it) comprises a stationary outer body or housing 13 having arotor cavity that is defined by an inwardly facing peripheral wall 14and a pair of axially spaced opposed side walls 16, only one of which isshown. The peripheral wall 14 is in the shape of a two-lobed epitrochoidor a curve parallel thereto and a rotor t8 having the general shape of atriangle with three convex peripheral faces 20 is mounted within therotor cavity on an eccentric 22 of a crankshaft 24. The crankshaft 24 isrotatably mounted outboard of the rotor cavity in the side walls 16 andaligned with the rotor cavitys axis.

-An annular externally toothed gear 26 is received about and isconcentric with the crankshaft 24 and is fixed to the engine housing 33.The gear 26 meshes with an internally toothed gear 28 that is concentricwith and fixed to the rotor 18. The gear 28 has one and one-half timesthe number of teeth as the gear 26 with the result that this gearingenforces a fixed cyclic relation between the rotor and the crankshaftsuch that the crankshaft which is the engines output makes threecomplete revolutions for every one complete revolution of the rotor. Therotor faces 20 cooperate with the peripheral wall 14 and with the sidewalls 16 to define three variable volume working chambers 30 that arespaced around and move with the rotor within the housing and vary involume as the rotor rotates about its axis while planetating withrespect to the crankshaft axis.

A carburetor 32 supplied with fuel from a fuel tank 34 by a fuel pump 36delivers a combustible air-fuel mixture to an intake manifold 38 underthe control of the carburetors throttle valve whose opening is controlled by a throttle lever 40 that is connected at one end to thethrottle valves shaft 41. The other end of lever 40 is connected to arod 42 that is linked to an accelerator pedal, not shown. for control bythe vehicle operator, the throttle valve arrangement being such that itis opened when the throttle lever is pivoted in a counterclockwisedirection as viewed in FIG. ll. The intake manifold 38 is connected toan intake port 44 which opens to the rotor cavity through the peripheralwall 14. On rotor rotation in the direction indicated by the arrow inFIG. 1, a combustible air-fuel mixture is sequentially periodicallyadmitted to the chambers 30 by the traversing motion of the rotor apexesrelative to the intake port 44 whereafter the airfuel mixture is trappedand then compressed in readiness for ignition. Sequential ignition ofthe air-fuel mixture in the chambers 30 is effected by two spark plugs46 and 48 which receive timed ignition pulses from a distributor 50 thatis driven by the crankshaft 24 as will be described in more detaillater. The two spark plugs 46 and 48 are on the side of the peripheralwall 14 opposite the side where the intake port 44 is located and areperipherally spaced thereabout so that the plug 46 is said to lead theother plug 48. The spark plugs 46 and 48 may be fired together or onlyone plug fired according to certain engine operating conditions. Withcombustion, the peripheral wall I4 takes the reaction to force the rotor38 to continue rotating and eventually each working chamber followingthe expansion phase, is exhausted during an exhaust phase to an exhaustmanifold 58 via an exhaust port 60 that is open to the rotor cavitythrough the peripheral wall 114 and is periodically traversed by therotor apexes.

Sealing of the working chambers 30 is effected by three apex seals 62each of which extends the width of the rotor and is mounted at one ofthe rotor apexes, six

crankshaft 24 at a speed proportional thereto and also provides a driveconnection between the crankshaft and the distributor shaft 52.

Referring to FIGS. 2, 3 and 4, pump shaft 78 has an expansible oilchamber 87 comprising an axially extending bore 88 and a pair ofradially extending bores 90 and 92. The radial bores 94]) and 92intersect the axial bore 88 at axially spaced points along the pumpshaft and are arranged 90 to each other with the bore 90 leading thebore 92 relative to the turning direction, as best shown in FIG. 3, forreasons which will become more apparent later. The radial bore 92extends completely through the shaft and is closed at one end by a pressfitted ball 94 and the other radial bore 90 extends only half-waythrough the pump shaft to meet with the blind lower end of axial bore88. The upper end of axial bore 88 is closed by a press fitted ball 95.The bore 90 corner seals 64 each of which is mounted in one of the rotorsides near one of the rotor apexes, and six side seals 66 each of whichis mounted in one of the rotor sides and extends adjacent one of therotor faces between two of the corner seals with the comer seals eachproviding a sealing link between adjacent ends of two side seals and oneapex seal. The apex seals 62 are urged radially outward by spring means,not shown, to continuously engage peripheral wall 14 and both the cornerseals 64 and side seals 66 on both rotor sides are urged axially outwardby suitable spring means, not shown, to continuously engage the sidewalls 16.

Having thus described a single rotor arrangement, it will be understoodthat the engine may have one or more additional rotors with suitableintake, ignition and exhaust provisions as is well known in the art. The

oil metering pump 12 according to the present invention is adapted tometer oil to either a single or dual rotor arrangement to lubricate'theapex seals 62 and also the corner seals 64 and side seals 66 to minimizethe wear of these gas seals and the rotor cavity walls. Describing nowthe oil metering pump 12, there is a pump body 68, which as best shownin FIG. 2, is sealingly fitted to a radially extending aperture 70 inthe engine housing H3 and retained therein by having a collar 72 fittingbetween the distributors base 74 and a boss 75 on the rotor housing 13.The pump body 68 is prevented from turning in aperture 70 by a pin, notshown. The pump body 68 has a cylindrical pump shaft bore 76 in which apump shaft 78 is rotatably mounted in axial alignment with thedistributor shaft 52. The distributor shaft 52 has a tongue 80 that isreceived within a slot 82 at the upper end of the pump shaft 78 and thelower end of the pump shaft 78 has a pinion 84 secured thereto thatmeshes with a worm gear 86 formed on the crankshaft 24. Thus, the pumpshaft 78 is driven by the serves as both an inlet to and an outlet fromthe chamber 87, as will be described in more detail later, and hencewill also be referred to as oil inlet-oil outlet port 90. The oilchamber 87 is expanded and contracted by a cylindrical plunger 96 which,as shown in FIG. 3, is mounted for reciprocal movement in the bore 92and operates to increase the volume of the oil chamber on radiallyoutward movement and decrease the volume on radially inward movement.

A plunger stroke control ring 98 is mounted in the pump body 68 aboutthe pump shaft 78 in an annular radially inwardly facing recess 10th asshown in FIGS. 2 and 3. The ring 98 has a radially inwardly facingcircular stroke control surface 102 arranged radially opposite theplunger 96. A spring 104 mounted in bore 92 between ball 94 and plunger96 biases the plunger radially outward to continuously contact thestroke control surface I02 of the stroke control ring 98. The strokecontrol ring 98 is guided for movement in fixed opposite radialdirections relative to the pump shaft 78 between positions where thestroke control ring is eccentric with respect to the pump shaft and isprevented from rotating relative to the pump shaft by a pair of guidepins R06. The guide pins 106 are arranged diametrically opposite eachother on opposite sides of the shaft 78 in axially extending holes inone radial wall of the recess I00 and are received in diametricallyopposite, radially extending slots 108 in the near side of the strokecontrol ring 98. Thus, the plunger 96 is caused to reciprocate as thepump shaft 78 turns with a plunger stroke that increases with increasingeccentricity of the stroke control ring 98 to provide a pumpdisplacement that increases with increasing eccentricity of the strokecontrol ring and a pump displacement per unit of time that increaseswith increasing pump shaft speed which is proportional to engine speed.

The eccentricity of the stroke control ring 98 is controlled by adisplacement control shaft 110 that is mounted in a bore 1 12 in thepump body 68 for turning about an axis aligned with the direction ofmovement of the ring 98. The displacement control shaft 110 has ahelical groove 114 which receives a pin 116 which is press fitted to thepump body 68 at right angles to bore 112 so that when the displacementcontrol shaft M0 is turned in the counterclockwise direction, as viewedin FIG. i, it advances leftward, as viewed in FIG. 3, to positively movethe displacement control ring 98 leftward to increase its eccentricityagainst the bias of a spring 118 that is mounted in a blind end radialbore 113 in the pump body 68 on the opposite side. The

spring 118 acts to maintain the ring 98 in contact with the shaft 1 1t)and thus move rightward when the shaft 110 is turned in the oppositedirection which has the effect of decreasing the rings eccentricity.

The shaft 110 is linked to the throttle linkage so that it is turned toincrease the eccentricity of the ring 98 as the throttle is opened. Asshown in FIGS. 2, 3 and 4, one end of shaft 110 extends outward of thepump body 68 and has secured thereto a lever 120, this connection beingmaintained by a nut 122 threaded to the outboard end of the shaft. Anoil ring 124 mounted in a circumferential groove in the shaft 110prevents oil leakage out of the bore 112. The other end of lever 120 hasa socket 126 pivotably secured thereto as best shown in FlG. 2. Thesocket 126 has an aperture 128 slidably receiving a rod 130 which at itsrighthand end has a snap ring 132 and receives a coil spring 134 betweenthe socket 126 and the snap ring 132 as shown in FIG. 1. The other endof rod 131 is pivotably secured to a lever 136 which is pivotallysupported on the carburetors throttle shaft 41 and is engaged by a tang138 on the throttle lever 411 to pivot counterclockwise with thethrottle lever as the throttle is opened. An adjustable stop provided bya stop screw 139 threaded to a boss on the pump body collar 72 engagesthe lever 120 to determine the maximum plunger stroke position asdescribed in more detail later. The displacement control shaft 1 isnormally biased to this minimum stroke position by a torsion spring 140which is arranged about the outboard portion of shaft 1 l0 and engagesat its opposite ends the pump body 68 and the lever 1211, as shown inFIG. 2, this torsion spring force urging clockwise turning of the lever120 and thus shaft 110 as viewed in FlG. 1. The coil spring 134maintains the lever 136 against the tang 138 and also yields to permitthe rod 130 to slide in socket 126 as the rod is pulled leftward beyondthe maximum travel of the displacement control lever 120.

Describing now how oil is supplied to the pump 12, metered and thendelivered to lubricate the engines gas seals, oil is obtained from theengines pressurized lubrication system which includes a passage 1561!.The pump body 68 has a radially extending oil supply passage 152 at thesame axial location as oil inlet-oil outlet port 90 that is open at itsouter end to an annular groove 154 which is aligned with the passage 150in the aperture 70 of the engine housing 13 with sealing in either axialdirection from this fluid connection being provided by a pair of oilring seals 156 that are received in circumferential grooves in the pumpbody 68 on either side of the groove 154. The pump body passage 152 atits inner end is open to a crescent shaped inlet recess 158 in the pumpshaft bore 76 which cooperates with the pump shafts outer surface toform an inlet port 160 that is thus connected to receive oil from theengine lubrication passage 150 and is centered on the line of movementof the stroke control ring 98., The pump shaft bore 76 further has apair of angularly spaced crescent shaped recesses 164 and 166 which alsocooperate with the external surface of the pump shaft 78 to form a pairof angularly spaced outlet ports 168 and 170 that are sealed from eachother and are angularly spaced and sealed from the inlet port 1611 bythe shaft 78 where it is received by the bore 76 as best shown in FIG.41. The inlet recess 158 extends through an arc of less than 180 and theoutlet recesses 164 and 166 each extend through an arc of less than 90with the outlet recesses centered apart and from the center of the inletrecess. Furthermore, all of the recesses 158, 16 1 and 166 and thus theoil inlet port 1611 and oil outlet ports 168 and 170 are at the sameaxial location as the oil inlet-oil outlet port 90. Thus, the oilinlet-oil outlet port 90 is sequentially opened to the inlet port andthen the oil outlet ports 168 and as the pump shaft 78 turns in thedirection of the arrow in FIG. 4. Furthermore, this arrangement placesthe oil inlet port 160 in a zone where the plunger 96 is moving radiallyoutward expanding oil chamber 87 and both the oil outlet ports 168 and170 in a zone where the plunger 96 is moving radially inward contractingoil chamber 87. The outlet ports 168 and 170 are open to the inner endsof oil delivery passages 172 and 174, respectively, which in turn areconnected to deliver oil to lubricate the engine. For example, an oilpipe 176 connects the oil delivery passage 172 to the carburetor 32 tosupply oil to the float bowl thereof, as shown in FIG. 1, while anotheroil pipe, not shown, connects the other oil delivery passage 174 tosupply oil to the carburetor for the other rotor. The oil thus deliveredis mixed with the fuel and then fed with the fuel through the intakeport to the rotor cavity where it is distributed to lubricate the gasseals as they slide on the housing walls. It will also be understoodthat the oil may be delivered directly into the carburetors jet circuitor into the air stream in the carburetor throat or directly to thehousing walls on which the seals slide.

Describing now the oil metering operation, the pump shaft 78 is driventhrough the worm gear drive by the engine crankshaft 24 at a speedproportional thereto and with the engine throttle closed and the engineidling the displacement control shaft 110 and thus the stroke controlring 98 at a minimum eccentric position, the plunger 96 by its rotationwith the pump shaft 78 is caused to reciprocate by being spring biasedto follow the stroke control rings circular cam surface 102. With oilmade available to the oil inlet passage 152 and thus to the inlet port160 and on initial communication of the oil inlet-oil outlet port 90with inlet port 160 and the port 911 leading the plunger 96 by 90, oilfills the oil chamber 87 as it expands with the plunger 96 movingradially outward. With continued turning of the pump shaft '78, the oilinlet-oil outlet port Q0 passes the inlet port 160 and then communicateswith the oil outlet port 168 with the shaft rotating as indicated inFIG. 4. At the same time, the plunger 96 is being caused by the strokecontrol ring 98 to move radially inward causing the oil to be displacedfrom the oil chamber 87 into the oil outlet port 168. With the oiloutlet ports 168 and 170 in the decreasing displacement zone, theplunger continues to move radially inward while the oil inlet-oil outletport 911 is closed off from the oil outlet port 168 and opened to theother oil outlet port 170 so that the latter port then receives theremaining half of the oil that is being displaced by the oil meteringpump. This oil metering rate is determined by sizing of the pump andcalibration thereof for the particular use to meet the minimum oilrequirements which occur at engine idle with no load demand. Then whenthe rotary speed of the pump shaft 78 increases with increasing enginespeed irrespective of whether the engine throttle is opened, the pumpingcycles per unit of time increase accordingly and thus the oil is meteredto the outlet ports 168 and 170 at a rate which increases withincreasing engine speed. When the engine throttle is opened, the pumpstroke and thus pump displacement increases irrespective of engine speedso that increasingly more oil is delivered. FIG. 3 shows the strokecontrol ring 98 in its maximum eccentric position which produces themaximum pump displacement. Thus, the oil is metered to the outlet portsat a rate which increases with both increasing engine speed and throttleopening and thus with engine load. It will also be understood that forengines where only one metered oil supply is required, the pump iseasily adapted thereto by simply connecting one of the oil outlet portsback to the oil inlet port 160 or by having only one oil outlet port.Furthermore, it will be understood that the oil supply to the pump maybe by gravity feed instead of by the engines lubrication pressuresupply.

The above described embodiments are illustrative of the invention whichmay be modified within the scope of the appended claims:

We claim:

1. in an oil metering pump for metering oil to lubricate a rotary enginehaving gas seals, an output shaft and a throttle,'a pump body having apump shaft bore, a pump shaft rotatably mounted in said bore, meansoperatively drivingly connecting said pump shaft to be driven by saidoutput shaft at a speed proportional thereto, said pump shaft having anoil chamber including a radial plunger bore, a plunger reciprocallymounted in said plunger bore operative to increase the volume of saidoil chamber on radially outward movement and decrease the volume onradially inward movement, a plunger stroke control ring mounted in saidpump body about said pump shaft having a radially inwardly facingcircular stroke control surface arranged radially opposite said plunger,means for biasing said plunger radially outward to continuously contactsaid stroke control surface of said stroke control ring, means forpreventing rotation of said stroke control ring while permittingmovement of said stroke control ring in fixed opposite radial directionsrelative to said pump shaft between positions where said stroke controlsurface is eccentric with respect to said pump shaft whereby saidplunger is caused to reciprocate as said pump shaft turns with a plungerstroke that increases with increasing eccentricity of said strokecontrol surface to provide a pump displacement that increases withincreasing eccentricity of said stroke control surface and a pumpdisplacement per unit of time that increases with increasing pump shaftspeed, means for increasing the eccentricity of said stroke controlsurface as said throttle is opened, an oil supply passage in said pumpbody for supplying oil to be metered, an oil delivery passage in saidpump body for delivering metered oil to lubricate the gas seals of theengine, said pump shaft bore having an inlet recess cooperating withsaid pump shaft to define an inlet port connected to said oil supplypassage, said pump shaft bore further having an outlet recesscooperating with said pump shaft to define an outlet port angularlyspaced from said inlet port, said outlet port connected to said oildelivery passage, all of said ports being located at the same axiallocation along said pump shaft, said oil chamber in said pump shafthaving an oil inlet-oil outlet port at the same axial location as saidinlet port and said outlet port for sequentially connecting said inletport to said oil chamber when said oil chamber is expanding and thenconnecting said oil chamber to said outlet port when said oil chamber iscontracting all during one pump shaft revolution whereby oil is meteredfrom said oil supply passage to said oil delivery passage at a rate thatincreases with increasing output shaft speed and throttle opening.

2. In an oil metering pump for metering oil to lubricate a rotary enginehaving gas seals, an output shaft and a throttle, a pump body having acylindrical pump shaft bore, a cylindrical pump shaft rotatably mountedin said bore, means operatively drivingly connecting said pump shaft tobe driven by said output shaft at a speed proportional thereto, saidpump shaft having an oil chamber including a cylindrical radial plungerbore, a cylindrical plunger reciprocally mounted in said plunger boreoperative to increase the volume of said oil chamber on radially outwardmovement and decrease the volume on radially inward movement, a plungerstroke control ring mounted in said pump body about said pump shafthaving a radially inwardly facing circular stroke control surfacearranged radially opposite said plunger, a spring mounted in said oilchamber for biasing said plunger radially outward to continuouslycontact said stroke control surface of said stroke control ring, meansfor preventing rotation of said stroke control ring while permittingmovement of said stroke control ring in fixed opposite radial directionsrelative to said pump shaft between positions where said stroke controlsurface is eccentric with respect to said pump shaft whereby saidplunger is caused to reciprocate as said pump shaft turns with a plungerstroke that increases with increasing eccentricity of said strokecontrol surface to provide a pump displacement that increases withincreasing eccentricity of said stroke control surface and a pumpdisplacement per unit of time that increases with increasing pump shaftspeed, a displacement control shaft mounted on said pump body engagingsaid stroke control ring, means for causing said displacement controlshaft to positively move said stroke control ring in one of its fixedradial directions to increase the eccentricity of said stroke controlsurface when said displacement control shaft is turned in one angulardirection, a spring mounted in said pump body for biasing said strokecontrol ring to follow said displacement control shaft and move in theopposite radial direction to decrease the eccentricity of said strokecontrol surface when said displacement control shaft is turned in theopposite angular direction, means operatively connecting said throttleand said displacement control shaft to vary the angular position of saiddisplacement control shaft with opening of said control valve whereinsaid displacement control shaft is turned in said one angular directionas said throttle valve is opened, an oil supply passage in said pumpbody for supplying oil to be metered, an oil delivery passage in saidpump body for delivering metered oil to lubricate the gas seals of theengine, said pump shaft bore having an inlet recess cooperating withsaid pump shaft to define an inlet port connected to said oil supplypassage, said pump shaft bore further having an outlet recesscooperating with said pump shaft to define an outlet port angularlyspaced from said inlet port, said outlet port connected to said oildelivery passage, all of said ports being located at the same axiallocation along said pump shaft, said oil chamber in said pump shafthaving an oil inlet-oil outlet port at the same axial location as saidinlet port and said outlet ports for sequentially connecting said inletport to said oil chamber when said oil chamber is expanding and thenconnecting said oil chamber to said outlet port when said oil chamber iscontracting all during one pump shaft revolution whereby oil is meteredfrom said oil supply passage to said oil delivery passage at a rate thatincreases with increasing output shaft speed and throttle opening.

3. In an oil metering pump for metering oil to lubricate a rotary enginehaving gas seals, ,an output shaft and a throttle, a pump body having acylindrical pump shaft bore, a cylindrical pump shaft rotatably mountedin said bore, means operatively drivingly connecting said pump shaft tobe driven by said output shaft at a speed proportional thereto, saidpump shaft having an oil chamber including a cylindrical radial plungerbore, a cylindrical plunger reciprocally mounted in said plunger boreoperative to increase the volume of said oil chamber on radially outwardmovement and decrease the volume on radially inward movement, a plungerstroke control ring mounted in said pump body about said pump shafthaving a radially inwardly facing circular stroke control surfacearranged radially opposite said plunger, a spring mounted in said oilchamber for biasing said plunger radially outward to continu ouslycontact said stroke control surface of said stroke control ring, meansfor preventing rotation of said stroke control ring while permittingmovement of said stroke control ring in fixed opposite radial directionsrelative to said pump shaft between positions where said stroke controlsurface is eccentric with respect to said pump shaft whereby saidplunger is caused to reciprocate as said pump shaft turns with a plungerstroke that increases with increasing eccentricity of said strokecontrol surface to provide a pump displacement that increases withincreasing eccentricity of said stroke control surface and a pumpdisplacement per unit of time that increases with increasing pump shaftspeed, a displacement control shaft mounted on said pump body engagingsaid stroke control ring, means for causing said displacement controlshaft to positively move said stroke control ring in one of its fixedradial directions to increase the eccentricity of said stroke controlsurface when said displacement control shaft is turned in one angulardirection, a spring mounted in said pump body for biasing said strokecontrol ring to follow said displacement control shaft and move in theopposite radial direction to decrease the eccentricity of said strokecontrol surface when said displacement control shaft is turned in theopposite angular direction, means operatively connecting said throttleand said displacement control shaft to vary the angular position of saiddisplacement control shaft with opening of said control valve whereinsaid displacement control shaft is turned in said one angular directionas said throttle is opened, an oil supply passage in said pump body forsupplying oil to be metered, a pair of oil delivery passages in saidpump body for delivering metered oil to lubricate the gas seals of theengine, said pump shaft bore having an inlet recess cooperating withsaid pump shaft to define an inlet port connected to said oil supplypassage, said pump shaft bore further having a pair of angularly spacedoutlet recesses cooperating with said pump shaft to define a pair ofangular spaced outlet ports angularly spaced from said inlet port, eachof said outlet ports connected to one of said oil delivery passages, allof said ports being located at the same axial location along said pumpshaft, said oil chamber in said pump shaft having an oil inlet'oiloutlet port at the same axial location as said inlet port and saidoutlet ports for sequentially connecting said inlet port to said oilchamber when said oil chamber is expanding and then successivelyconnecting said oil chamber to said outlet ports when said oil chamberis contracting all during one pump shaft revolution whereby oil ismetered from said oil supply passage to said oil delivery passages at arate that increases with increasing output shaft speed and throttleopening.

1. In an oil metering pump for metering oil to lubricate a rotary enginehaving gas seals, an output shafT and a throttle, a pump body having apump shaft bore, a pump shaft rotatably mounted in said bore, meansoperatively drivingly connecting said pump shaft to be driven by saidoutput shaft at a speed proportional thereto, said pump shaft having anoil chamber including a radial plunger bore, a plunger reciprocallymounted in said plunger bore operative to increase the volume of saidoil chamber on radially outward movement and decrease the volume onradially inward movement, a plunger stroke control ring mounted in saidpump body about said pump shaft having a radially inwardly facingcircular stroke control surface arranged radially opposite said plunger,means for biasing said plunger radially outward to continuously contactsaid stroke control surface of said stroke control ring, means forpreventing rotation of said stroke control ring while permittingmovement of said stroke control ring in fixed opposite radial directionsrelative to said pump shaft between positions where said stroke controlsurface is eccentric with respect to said pump shaft whereby saidplunger is caused to reciprocate as said pump shaft turns with a plungerstroke that increases with increasing eccentricity of said strokecontrol surface to provide a pump displacement that increases withincreasing eccentricity of said stroke control surface and a pumpdisplacement per unit of time that increases with increasing pump shaftspeed, means for increasing the eccentricity of said stroke controlsurface as said throttle is opened, an oil supply passage in said pumpbody for supplying oil to be metered, an oil delivery passage in saidpump body for delivering metered oil to lubricate the gas seals of theengine, said pump shaft bore having an inlet recess cooperating withsaid pump shaft to define an inlet port connected to said oil supplypassage, said pump shaft bore further having an outlet recesscooperating with said pump shaft to define an outlet port angularlyspaced from said inlet port, said outlet port connected to said oildelivery passage, all of said ports being located at the same axiallocation along said pump shaft, said oil chamber in said pump shafthaving an oil inlet-oil outlet port at the same axial location as saidinlet port and said outlet port for sequentially connecting said inletport to said oil chamber when said oil chamber is expanding and thenconnecting said oil chamber to said outlet port when said oil chamber iscontracting all during one pump shaft revolution whereby oil is meteredfrom said oil supply passage to said oil delivery passage at a rate thatincreases with increasing output shaft speed and throttle opening.
 2. Inan oil metering pump for metering oil to lubricate a rotary enginehaving gas seals, an output shaft and a throttle, a pump body having acylindrical pump shaft bore, a cylindrical pump shaft rotatably mountedin said bore, means operatively drivingly connecting said pump shaft tobe driven by said output shaft at a speed proportional thereto, saidpump shaft having an oil chamber including a cylindrical radial plungerbore, a cylindrical plunger reciprocally mounted in said plunger boreoperative to increase the volume of said oil chamber on radially outwardmovement and decrease the volume on radially inward movement, a plungerstroke control ring mounted in said pump body about said pump shafthaving a radially inwardly facing circular stroke control surfacearranged radially opposite said plunger, a spring mounted in said oilchamber for biasing said plunger radially outward to continuouslycontact said stroke control surface of said stroke control ring, meansfor preventing rotation of said stroke control ring while permittingmovement of said stroke control ring in fixed opposite radial directionsrelative to said pump shaft between positions where said stroke controlsurface is eccentric with respect to said pump shaft whereby saidplunger is caused to reciprocate as said pump shaft turns with a plungerstroke that increases with increasiNg eccentricity of said strokecontrol surface to provide a pump displacement that increases withincreasing eccentricity of said stroke control surface and a pumpdisplacement per unit of time that increases with increasing pump shaftspeed, a displacement control shaft mounted on said pump body engagingsaid stroke control ring, means for causing said displacement controlshaft to positively move said stroke control ring in one of its fixedradial directions to increase the eccentricity of said stroke controlsurface when said displacement control shaft is turned in one angulardirection, a spring mounted in said pump body for biasing said strokecontrol ring to follow said displacement control shaft and move in theopposite radial direction to decrease the eccentricity of said strokecontrol surface when said displacement control shaft is turned in theopposite angular direction, means operatively connecting said throttleand said displacement control shaft to vary the angular position of saiddisplacement control shaft with opening of said control valve whereinsaid displacement control shaft is turned in said one angular directionas said throttle valve is opened, an oil supply passage in said pumpbody for supplying oil to be metered, an oil delivery passage in saidpump body for delivering metered oil to lubricate the gas seals of theengine, said pump shaft bore having an inlet recess cooperating withsaid pump shaft to define an inlet port connected to said oil supplypassage, said pump shaft bore further having an outlet recesscooperating with said pump shaft to define an outlet port angularlyspaced from said inlet port, said outlet port connected to said oildelivery passage, all of said ports being located at the same axiallocation along said pump shaft, said oil chamber in said pump shafthaving an oil inlet-oil outlet port at the same axial location as saidinlet port and said outlet ports for sequentially connecting said inletport to said oil chamber when said oil chamber is expanding and thenconnecting said oil chamber to said outlet port when said oil chamber iscontracting all during one pump shaft revolution whereby oil is meteredfrom said oil supply passage to said oil delivery passage at a rate thatincreases with increasing output shaft speed and throttle opening.
 3. Inan oil metering pump for metering oil to lubricate a rotary enginehaving gas seals, an output shaft and a throttle, a pump body having acylindrical pump shaft bore, a cylindrical pump shaft rotatably mountedin said bore, means operatively drivingly connecting said pump shaft tobe driven by said output shaft at a speed proportional thereto, saidpump shaft having an oil chamber including a cylindrical radial plungerbore, a cylindrical plunger reciprocally mounted in said plunger boreoperative to increase the volume of said oil chamber on radially outwardmovement and decrease the volume on radially inward movement, a plungerstroke control ring mounted in said pump body about said pump shafthaving a radially inwardly facing circular stroke control surfacearranged radially opposite said plunger, a spring mounted in said oilchamber for biasing said plunger radially outward to continuouslycontact said stroke control surface of said stroke control ring, meansfor preventing rotation of said stroke control ring while permittingmovement of said stroke control ring in fixed opposite radial directionsrelative to said pump shaft between positions where said stroke controlsurface is eccentric with respect to said pump shaft whereby saidplunger is caused to reciprocate as said pump shaft turns with a plungerstroke that increases with increasing eccentricity of said strokecontrol surface to provide a pump displacement that increases withincreasing eccentricity of said stroke control surface and a pumpdisplacement per unit of time that increases with increasing pump shaftspeed, a displacement control shaft mounted on said pump body engagingsaid stroke control ring, means fOr causing said displacement controlshaft to positively move said stroke control ring in one of its fixedradial directions to increase the eccentricity of said stroke controlsurface when said displacement control shaft is turned in one angulardirection, a spring mounted in said pump body for biasing said strokecontrol ring to follow said displacement control shaft and move in theopposite radial direction to decrease the eccentricity of said strokecontrol surface when said displacement control shaft is turned in theopposite angular direction, means operatively connecting said throttleand said displacement control shaft to vary the angular position of saiddisplacement control shaft with opening of said control valve whereinsaid displacement control shaft is turned in said one angular directionas said throttle is opened, an oil supply passage in said pump body forsupplying oil to be metered, a pair of oil delivery passages in saidpump body for delivering metered oil to lubricate the gas seals of theengine, said pump shaft bore having an inlet recess cooperating withsaid pump shaft to define an inlet port connected to said oil supplypassage, said pump shaft bore further having a pair of angularly spacedoutlet recesses cooperating with said pump shaft to define a pair ofangular spaced outlet ports angularly spaced from said inlet port, eachof said outlet ports connected to one of said oil delivery passages, allof said ports being located at the same axial location along said pumpshaft, said oil chamber in said pump shaft having an oil inlet-oiloutlet port at the same axial location as said inlet port and saidoutlet ports for sequentially connecting said inlet port to said oilchamber when said oil chamber is expanding and then successivelyconnecting said oil chamber to said outlet ports when said oil chamberis contracting all during one pump shaft revolution whereby oil ismetered from said oil supply passage to said oil delivery passages at arate that increases with increasing output shaft speed and throttleopening.